Gearless variable speed transmission



July 6, 1937. F. w. sl-:ECK

v GEARLESS VARIABLE SPEED TRANSMISSION 'r sheets-sheet 1 'Filed Jan. 21. 1936 u Hymne IQ Q mk IN 'tl IIW: Il N l s 7 l n, l I, n@ m Q s .Q u Q w,

www NN, MQQ Tw July 6,1937. F. w. sEEcK v 2,085,770:

GEARLESS VARIABLE SPEEDTRANSMISSIN Filed Jan., 21, 193s 7 sheets-sheet 2 .III A July 6', 1937. F. w. sEEcK I V GEARLESS VARIABLE SPEED TRANSMISSION I Filed Jain.' 2.1. 1936 l visneefc's-sheet 3- INI/ElvToR.A y Ew/#M/f/Mwi' ATTORNEYS.. y.

/ V I il July 6', 1937. E. W. SEC'K GEARLEss'vARmBLE-sPEED TRANsMrssIoN -Filed Jan. -21. 11936 'r sheets-sheet sA S. m R w. .T A.

July 6, 1937. F. w. sEEcK 2,085,770

AGEARLESS VARIABLE SPEEDTRANSMISSION Filed Jan.y 21,' 1956 'r sheets-sheet 'r Patented July 6, 1937 UNITED STATES GEAnLEss vanm' SPEED. TRANSMIS- Ferainand vv. seeek, Lebanon, oreg.

Application January 21,1936, Serial No. 60,030

' 12 (cl. 'i4-69) One of the principal objects of my invention is to provide a gearless transmission for a one-way motor which is adapted to transmit the driving power, by positive drive, from the driving shaft to the driven shaft at controllable variable speeds, and by means which will not result in a jerky transmission of power from the motor, but instead will cause the driven shaft to be operated evenly, smoothly and quietly.

l() A further object of my inventionis so to arrange the power transmitting elements that the transmission may be varied-gradually increasedA or diminished-manually. and automatically without discontinuing the transmission of power from. the motor to the driven shaft of my transmission.

A further object of my invention is to provide a transmission composed of. few parts, and these of simple, strong and durable construction and easily arranged in operative assembly.

A further object of myinvention is to provide a transmission of compact form so that it may vbe installed in limited spaces.

The foregoing and incidental features of my 25 invention are hereinafter fully described with reference to the accompanying' drawings.

-In the drawings:

Fig. 1 (Sheet l) is an outside view of the casing or housing in which my variable speed power the interior of my transmission and housing' 40 taken on a plane' indicated by 3-3 of Fig. 2 and looking in the direction indicated by the arrows;

Fig. 3a (Sheet 2) is a section on a plane indicated by 3a-3a of Fig. 2, but looking in the direction opposite to that of Fig. 3, as indicated by the arrow but showing an active phase of my' transmission;

Fig. 4 (Sheet 1) is a horizontal section taken thru the center of Fig. 1 but drawn on the same scaleas Figs. 2 .and 3, the section corresponding to the plane 4-4 indicated in Fig. 3, looking in the -direction pointed by the arrows j Fig. 5 (Sheet 3) i's a vertical section taken on the plane indicated by 5-5 in Figs. 2 and 4 (Sheet 1) and looking in the directions indicated by the arrows, thus in the same direction as Fig. 3;

Fig. 6 (Sheet 3) is a vertical section taken on the plane indicated by 6-6 in Fig.' 2', and looking in the directions indicated by the arrows,

' thus in the 'same directions as in Figs. 5 and 3;

Figs. 7, a (Sheena), 9, 1o (sheet 4)-11 (sheet transmission is inclosed, the. interior of which 2), 12,-13, 14 (Sheet 3), 15, '(Sheet 4), 16 and 17 (Sheet 5), are views in perspective oi details of my transmission; and

Figs. 18, 19, 20, 21 (Sheet 5), 22 (Sheet 7) 23, 24 (Sheet 6) and 25 (Sheet 7) are diagrammatic 5 illustrations of the operation of my transmission.

Referring first to Figs. l, 2, and 4: The housing or casing of my transmission is divided into two sections a and b, rigidly fastened together by bolts athru their companion annular flanges lo a2, b2. The housing is also rigidly attached to any convenient supporting frame by any suitable means, the means and the supporting frame n not being shown in the drawings. The driving shaft 2 is assumed to be operatively connected to- 1I a motor. 3 indicates the drivenshaft to which power is to be transmitted from driving shaft 2. Suitable bearings are provided as indicated at b3, between the rear'sec'tion b of the housing` and the driven shaft 3; and at a3 between the 20 front section a of the housing anda cup-shaped transmission member c keyed to the driving shaft 2 (Fi'g. 17). The section b of the housing is made with a portion of its periphery inwardly offset as shown 25 at b4 in Figs. l and 4, to accommodate an an-` nular memberj (shown in detail in Fig. 9) mounted thereon. A collar b5 threaded on the outer. end ofthe oilset portion b4 of the housing section b holds the annulary member a' in place. 30-

The annular member y' is adapted to be partially rotated in either direction by means of a pivoted lever k (see Figs. 1 and 3).

The lever 1c is made with a lug k' adapted to 5 be engaged with slots k2 provided in a segmental 35 peripheral ange k3 integral with housing section b (see details Figs. 3 and 10). The en gagement of the lug k with one of the slots k2 thus holds the annular member i against rota- The interior of the housing section b is cast y with two annular concentric flanges u. and 'D (see Figs. 2 and .4) The inner periphery of the outer ilange w, and the outer periphery of the inner ange v are made with regularly spaced opposed 45 cam, lock` recesses w, w (see Fig. 10) extending in the same direction.

The inner end of the driven shaft 3 is provided with a central hub q, and a concentric peripheral flange r, as shown in Figs. 2,'4, and 15. The (ip-60 posed faces of the hub q, and the inner periphery of the ange r are mad'ewith opposed cam lock recesses t, t (see Fig. 15).,extending in the same direction. These cam lock. recesses correspond with'those of the flanges u. and v of the housing 55.

section b (see Fig.'10) but extend in an oppositeV direction as shown by Fig.- 5.

The central portion of housing vsection b, as shown in'Figs. 2 and 4, provides a-journal bearing for the driven shaft 3 including ball bearings b3, 00

as mentioned. Between the outer periphery of the flange r of shaft 3, and the inner periphery of flange v of the housing section Z7I are ball bear-- ings v2, as indicated -in Figs. 2 and 4.

Figs. 11, 12, 13, and 14 (Sheets 2 and 3) show views of four annular clutch rings m, n, o, p, respectively. The member n. (Fig. 12) is rotatably seated in member m (Fig. 11) and the members m and n so assembled are inserted between the cam lockrecesses w, 1v oi the flanges u and v of the housing section b (see Figs. 10 and 5) and likewise clutch member p is rotatably seated in member o, and the members oand p so assembled are inserted between the cam. lock recesses t, t' of the center hub q of the driven shaft 3 and its concentric flange r' (see Figs. 15 and 5). The described arrangement of the clutch members m, 'n and 0, p will be seen in Fig. 5.

, clutch member m. with the flange u, when the clutch member m attempts to tum in one direction, and 'similarly to engage the clutch Ato member n with the flange v of the case section b, when clutch member n attempts to turn in one direction. Thus from Fig. 5 it is apparentthat clutch rings m and n may rotate freely,

independently, clockwise within case section b, but rotation of either or both counterclockwise would cause the cam rollers s to effect the engagement of clutch rings m and n with the anges u, v, respectively, of case section b.

Similarly, clutch rings o` and .p are free to rotate, independently, counterclockwise, without engaging with hub q or hub flange T of -driven shaft 3, but rotation clockwise of either or both of these clutch rings will effect such engagement and cause the rotation ofdriven shaft 3 in the same direction.

vThe clutch rings o and p are provided with pins o2 and p2, respectively, as shown in Figs. 13 and 14; the pins being so located that both are the same distance fromthe center, as shown in Fig. 6, and 'on the pins o2 and p2 are mounted The clutch rings m and n are each provided with a" radial guideway consisting of parallel guide flanges m' and n', see Figs. l1 and 12extending inward from their perimeters, and joined respectively bywebs m2 and n2.

An equalizing or coupling ring f (Fig. 8) is made with radial guideways comprising guide anges f3, in which guideways the rollers o3 and p3, mounted on the pins o2, p2 of the clutch, vrings o, p, respectively, travel, as shown in Figs.

. 3 and 3a.

Coupling ring ,f is further madewith two opposite radial ribs f4, integral with the anges f3, and perpendicular therewith, as shown in Figs.

3a and 8. These radial ribs f4 have pins f2 lol cated equal distances from the center, and on these pins are mounted rollers m3 and 113re- `spectively, the roller m3 traveling in the guideway m' of clutch ring m, and the roller n3 travel-` (See Figs.

The interior of the cylindrical wall c6 of transmission member `c, as shown in Fig. `1'7, is madeY with two equal, opposite plane-face surfaces c' parallel to each other, and perpendicular tothe diameter drawn to their centers, and both sur-f vfaces are made with central rectangular recesses dicular arms g' of the ring or annular actuating plate g, shown in Fig. 16. Actuating plate q thus rotates with transmission member c, but at the same time may be moved in and out relatively to the transverse wall c1 of transmission member c. l

Coil springs g2, see Fig. 4, are'placed-on'the slots c4 of transmission member c, with one end bearing against the face'oi the actuating plate a. lThese coil springs g2 normally space the actuating plate g from transmission member c. The inner faces of the arms g of actuating plate g (see Fig. 16) are madewith rectangular oblique cross grooves or guideways g3. l

Within transmission member c and between the connecting arms o" of actuating plate q is placed the elliptical plate d (see Fig. '7) which ment o! the balance plate with reference lto the Within transmission member c is alsolocated an elliptical ring, or coupling member le (Fig. '1), the-interior face e' of which is circular, and the outer face'l e3 elliptical, which outer face e3 corresponds with the rim Aface ofthe balanceplate d, and is of the same size. The oppositeouter parallel plane faces of coupling member' e are grooved so as to produce rectangular parallel obliquely sloping guide ribs e4 running in opposite direction to the guide ribs d2 of balance plate d. Both the balance plate d and the companion coupling member e slide in the grooves/ a3 of the arms g of actuating plate kg; but the movement of actuating plate b towards and from transmission member c will cause. balance plate d and coupling member e to move in opposite directions, in parallel vertical planes.v l

The coupling. ring f (Fig. 8) -is'rotatably supported within coupling member e, and suitable ball bearings e2 -are interposed between these parts as seen in Figs. 2, 3, and 4.

An annular positioning plate h (see Fig.v 16) bears on actuating plate g, there being ball bearingh3 between them, see Figs. 2 and 4. The outer periphery of 'plate h is provided with equally spaced peripheral segmental flanges h.

', The set-in wall b4 of housing section b has 4spaces b5 (see Fig. l0) thru which spaces said ilanges h' of positioning plate h project. The outer faces of said 'iianges rh' are made with spiral ribs h4 constituting guide-elements, which By the spiral rotation of member i, by hand lever k, positioning plate h maybe spirally moved inward .towards member c, moving with' it the actuating plate g. Since the guide elements g3 on the inner faces of arms g of the actuating plate g cooperate with guide elements d2, e4 of balance plate d and transmission member e, respectively, therefore, the movement of the actuating plate g inward causes the said members d and ev to be moved radially inward in opposite directions, and to become inactively'positioned, that is, concentric with the axis of rotation of member c, as shown at Fig. 3. When, by means of hand lever 1c, the member :i is given a partial Vrotation in the opposite direction moving positioning plate h away from transmission member c, the pressure of springs g2 will normally cause the actuating plate g also to follow positioning plate h in moving away from member c, which movement in turn will cause members d and e to return towards their eccentric positions. Also, depending largely upon the speed of the. motor, the pull of centrifugal force on members d ande particularlyon the former, will aid the springs g2 in moving actuating plate g away from member c. This particular feature is mentioned later.

The arms g of actuating plate g (Fig. 16) bear in recesses c2 and project thru slots c3 of transmission member e (seeFig. 17), and thus actuating plate g rotates with member c. tioning plate h does not rotate with actuating plate g and is separated from the latter by ball bearings h3 as mentioned.

OpeTatirmf-.When balance plate d and coupling member e, and with the latter the coupling ring f, register concentrically with the axis of rotation of primary transmission member c, in the position as shown by Fig. 3, my transmission is idling; the primary transmission member c, coupling member e, and'actuating plate g merely idling about the coupling ring f, without causing any movement of the latter. It is assumed the driving shaft 2, the transmission member c, balance plate d, coupling member e, and actuating plate g are being rotated in a clockwise direction as viewed in Fig. 3.

From the idling, or-neutral position just described and illustrated in Fig. 3, let it be assumed that, thru the manipulation of` lever 1c, and member i and the action of springs g2, the members h. g, and e are placed in their active position, as previously explained, and the coupling ring fis thrown into extreme eccentric, active position, for example as indicated in Fig. 18. The coupling ring f will then no longer be concentric with transmission member c, vand it will beapparent that now, astransmission member c Vrotates in a clockwise direction, as indicated by the arrow in Fig. 18, the center of the coupling ring f will revolve in a circular path about the axis of rotation of primary transmission member c, and coupling ring f -similarly will follow a circular path. As transmission member c rotates in a clockwise direction,l from its position in Fig. 18 to that indicated in Fig. 19, the coupling ring fis moved slightly to the right and slightly downward from its position of Fig. 18, and as member `c continues its rotation from theposition in Fig.

19 to that in Fig. 20, .coupling ring f is. moved downward and to the left, and then, from the position in Fig. 20 to that in Fig. 2l, coupling Posiring fis moved upward and to the left, and so on.

Now, as coupling ring f is moved from the position in Fig. 18 to that in Fig. 19, that iS to the right and downward, it tends to move therollers m3 and n3, carried on pins l2 of coupling ring f,

to the right. Moving roller m3 to the right will cause clutch ring m to be turned clockwise, since the roller m3 bears in the guideway m' of clutch ring m. Similarly, moving roller n3 to the right, when n3 is in the position shown in Fig. 18, would cause clutch ring n to be turned in a counterclockwise direction. Now, referring to Fig. 5, it is apparent that clutch ring m is free to turn in a clockwise direction, but that clutch ring n cannot turn in a counterclockwise direction, since such movement would cause 4clutch ring n to bind with flange v, thru the rollers s in the cam-lock recesses w'. Consequently, ascoupling ring f is moved from the position in Fig.

, 18 to that in Fig. 19, the roller n3 is held against movement to the right,'with thelresult that the coupling ring f is forced to turn or rotate slightly' in a clockwise direction. From the position in Fig. 19 the coupling ring f moves downward and to .the left to the position shown in Fig. 20..

the. cam-lock recesses w. On the other hand,

moving roller n3 to the left willcause clutch ring n to be turned in a clockwise direction, which it is free to do as evident from Fig. 5. Consequently, during this phase the roller m3 is held against movement to the left, thereby forcing -the coupling ring to rotate slightly further in a clockwise direction.

In a similar manner, by following the paths 'of' the coupling ring f and the rollers m3 and 'n3 thru the -various positions indicated in the Figs). 18 to 22, itwill be found that rollers m3 and n3 alternately hold, and thus alternately force the coupling ring f to make a further partial rotation in a clockwise direction. The result is that as long asy coupling ring f remains in its eccentric position, and thus revolves in a circular by the cooperation of the rollers m3, n3 and the clutch rings m and n is further illustrated with reference to Fig. 23.

In Fig. 23, a: indicates the' coincidingcenters of rotation of driving shaft 2, driven shaft 3,

Aand rotating member c (fast on driving shaft 2 as above described). In the various positions of the coupling ring f. shown in Figs. 18 to 22, the center of said coupling ring, due to its eccentric position, follows a circular path, which is indicated by the circle z in Fig. 23,. vSince the rollers m3 and 11.3 are mounted on the pins f2 .of the alined radial ribs fl (Fig. 8) of the coupling ring f, it is obvious that a line connecting the centers of m3 and n3 must always pass thru the center of the coupling ring. f; in other words, such line must always intersect or touch the .circle z. When the coupling ring f is` in the position shown in Fig. 18, rollers 11,13 and 113 are in vertical alinement,.as indicated in Fig. 23 by the points 1112i and 112|, and the center of the ring f is at the point z2 I. As center of the coupling ring f moves in a clockwise direction about the circle z, 113,

being prevented by clutch member 11 from moving to the right; moves downward on line 2 in the guideway 11' of clutch member 11, and m3 moves to the right, as previously explained with reference to Fig. 19. It is obvious that m3 will continue to be pushed to the right until the center of f has moved around to the position 222, by which time m3 will have moved to the position of m22, and the line 1122-11122 will be tangent to the circle z at the point 222. The center of l continues moving in a clockwise direction; m3 is held by clutch member 111 against movement to the left, but 113 can now slip in clockwise direction and will continue moving until the center of f reaches the point 223 and,113 reaches the point 1124, the line 1124-m22 being tangent to circle z at z23. During this interval roller 1113, sliding in the guideway m' of clutch member m, has moved down and back on the line 3. Now clutch member 11 again holds and roller m3 slips clockwise from point m22 to point m24 until the center oi.' coupling ring f reaches point 224, and so on. By simple geometrical proof, angles 1'122-m22-1124 and m22-1124-1n24 are equal, arcs 222-223 and 223-1124 (measured in clockwise direction) are equal. Furthermore, it is obvious that, since the center of f moves at uniform speed around circle z. 113, moving from point 1122 to 1124 while the center of f moves from 222 to 223, moves fastestat the center of its arc, that is.- at the point 1125, and slows down again to a state of rest at 1124. (Whenf113 is at point 1125, m3 has slid down to point'm25.)

From this illustration, the following correct deductions are to be made regarding the relative movements of clutch rings m and n and the corresponding rollers 1113 and 113 carried by the -coupling ring f (as long as the circle z in which clockwise direction. Since l is caused to. rotate,

the rollers o3 and p3 and with them the clutch rings o and p are also turned in clockwise direction by f as indicated in Figs. 18 to' 22. It is apparent from Fig. 5-that if clutch ring o moves in clockwise direction, it will engage with the hub flange 1' due to the locking action of the rollers s in the cam-lock recesses t' of the flange r. Similarly, if clutch ring p moves in clockwise direction, it will engage with the hub q thru the locking action of the rollers s in the cam-lock recesses t of hub q. Thus, if either clutch ring o or clutch ring p turns in clockwise direction, it

will force the driven shaft 3 to rotate with it in Aa clockwisefdirection. If both clutch rings o and p are turning at different rates of speed, in a clockwise direction, whichever one is turn- ,ing the faster at the particular moment will be driving the shaft 3 at that particular speed. The

pins o2, p2 thus function alternately as crank pins for the driven shaft 3.

` cular path y, as coupling ring f rotates.

The relative movements of the rollers o3 and p3, that is the movements of the crank pins o2, p2, as indicated in Figs. 18 to 22, may be illustrated in connection with the movements of rollers m3 and 113 by referring to Fig. 24.

In Fig. 24 the center circle z, and points to indicated in Fig. 23. Due to the construction of clutch members o and p (Figs. 13 and 14) the pins o2, p2 and therefore the rollers'03, p3 mounted thereon are equi-distant from the center of rotation of the shafts 2 and 3 and transmission member c, that is, are both equi-distant from center :v (Fig.,24), and therefore move around :c in a cir- Itis obvious from .the construction of the coupling ring f (Fig. 8), `with its webs f3 and radial ribs f4, that the line connecting the centers of rollers o3 and 113 will always pass thru the center of coupling ring j, tliat is will' always intersect or touch whichrollers m3 and 113 move are the same as `circle zin Fig. A241, and furthermore, will always be perpendicular to the line passing from the center of m3 to the center of 113.

In Fig. 24 when rollers 113 and m3 are at the points marked 1112i and 112 i rollers o3 and p3 will. be at the points indicated by 02| and 112|, that is the line 02|-p2l must be perpendicular tov the line m2I-112l at a pointwhere it intersects the circle a. Now 113 is held against movement to the right and slides downward to the position indicated by1122, and m3 moves to the point m22, as in Fig. 23. Under` this condition rollers o3 and'p3 must move to such points as 022 and 1122, respectively,-that is the line 022-1122 must be perpendicular to the line 11122-1122 at the point where the latter line touches the circle 2, and the line 022-1122 must go thru the center z. At this phase m3-is held at m22 against movement to the left, as explained with reference to Fig. 23, and 113 then slides clockwise from 1122 until it comes to rest at 1124. When 113 reaches the middle point of its arc 1122-1124, at'the point 1125, and is therefore traveling fastest, 03 and 113 are in the positions 023 and p23, respectively, since the line o23-p23 must be perpendicular to the li'ne m25-1125. Similarly, when 113 reaches the point 1124,03 and 113 will be in the positions of 024 and p24, respectively.v

By simple geometric proof it can be shown that arc 022-023 equals arc 1123-1124, and equals arc r o2 l-o22, and that arc 023-024 equals arc :122-1123, and so on.

Thus when 113 moves from point 1122 to point 1125, o3 moves from point 022 to point o23 and p3 slides back from point 1122 to point p23; then, as 113 continues to move from point 1125 to point'1124, o3 slides back from point 023 to point 024 and p3 moves from point p23 to point p24. When 113 is moving fastest (i. e. at point 1125 at the center of its are 1122-1124) o3 has slowed down and p3 begins to move forward and moves thru an equal distance in the same length of time as 03 ha done previously.

When the coupling ring f is rotating fastest, that is when either of m3 or 113 is moving fastest, it is driving rollers 03 or p3, and therewith clutch rings o and p and driven shaft 3 the slowest, altho always at a speed greater than f, and when'the coupling ring f is turning the slowest the reverse is true. Inthis way the coupling ring f produces a resulting equalizlng effect on the speeds at which rollers o3 and p3 and therewith clutch rings o and p alternately4 are driven, and thus on the speed at which shaft 3 is driven.

` ing atits greatest speed; o decreases, n increases;

when n reaches its greatest speed, and o has .slowed down, clutch ring p in turn begins to drive shaft 3 and begins to increase its speed and continues to increase, while n decreases, until p reaches its greatest speed, when n comes torest and m begins to move;` then m increases as p decreases, etc. Since the periods of movement of m and n andthe arcs thru which they move are always the same (so long as the coupling ring f remains in the same eccentric position) there is perfect synchronization, by means of the coupling ring f, among the clutch elements m, n, o, andV isf-which constitutes the most important feature of my invention.

When the driving shaft 2 is rotating rapidly the succession' of driving impulses imparted to the driven shaft 3 by the clutch rings o and p alternately causes the latter to be given very smooth running motion.

' Figs. 18, 19, 20, 21, and 22 illustrate the operation when the coupling ring f is'in extreme eccentric position. In this position the driven shaft 3 is given its greatest rate of speed.. If the coupling ring-f be moved into less eccentric position, the clutch rings m, n, o, and p would of course be rotated in shorter arcs, and the coupling ring f would rotate more slowly. In such case thespeed of the driven shaft 3 would be,

correspondingly reduced. Thus by adjusting the eccentricity of the coupling ring f, by means of hand lever k, as above described,relatively to the axis of rotation of driving shaft 2-the speed of the driven shaft 3 may be controlled.

Due to the relative sizes of the parts of ymy transmission, and as apparent from Figs. 18 to 22, the coupling ring f rotates approximately a quarter of a turn while the transmission mem- 'ber c rotates one complete turn. But bymaking the latter member c and coupling member e,

and thecooperating parts of my transmission relatively larger than the coupling ring f, it is possible to provide a construction which causes member f to rotate more rapidly, and thus drive driven shaft 3 at a correspondingly greater speed.

In Fig. 24, m3 and n3 are illustrated as being agreater distance apart than the diameter of the circle in which o3 and p3 move. I have found it most satisfactory to have the ratio of the distance between o2 and p2 and the distance between the pins f2 of the rollers 'm3 and n3 (see Fig. `6) of approximately the proportion of 6 to '7. However, the proportion may be varied and` my invention is not to be understood as limited to any specific dimensions or relative proportions. But it is necessary in my invention that o2 and p2should be equi-distant fromthe axes of rotation of shafts 2 and 3, and that m3 and n3 should be equi-distant from the center of f; also, of course, that o2 and p2 should be dia'- metrically opposite each other, that m3 and n3 should be diametrically opposite each other, and that the line connecting o2 and p2 should be perpendicular tothe line connecting m3 and n3.

In Figs. 23 and 24 the circle z described by the center of f is comparatively large, that is to say, the coupling ring f has been moved into very eccentric position. Fig. 25 illustrates the action cf the clutch members when f is in less eccentric position, that is, when the circle z described by the center of f is smaller. The same characters are used to designate the positions of m3, n3, o3, and p3 in Fig. 25 as in Figs. 23 and 24, and the same observations regarding the relative movements of m3, n3, o3, and p3 may -lbe made. It

will be noticed, however, that'the distances of travel of the driving elements 03 and p3 (and also of m3 and 11.3) are considerably less. In other words, the speed with which shaft 3 -is driven thru the medium alternately of clutch members 0 and p has been reduced by decreasing the eccentric position of the ring f. But the synchronization of the various clutch members has in no way been disturbed.

The manipulation of the hand lever k acts, thru the intermediary of various members in the manner already described, to limit the eccentricity of the coupling ring f and thus to control the speed at which the shaft 3 can be driven. However, an important feature of my transmission is that the speed control is-also to a large extent automatic. It has been assumed, for the sake of simplicity in explaining the movement of the clutch rings and coupling ring of rny transmission, that the coupling ring f is moved from its idling or neutral position immediately into extreme active eccentric position. Actually this would,y not occur, particularly if there were a relatively heavy pull on the driven shaft 3', and such sudden movement of coupling ring f into extreme eccentric position would tend to stall the engine and would at best result in an undesirable jerk and strain on the transmission and motor. But when it is attempted by such manipulation of the lever k to move the coupling ring f from neutral to extreme eccentric position, the resistance set up by the shaft 3 tends to oppose the action of the' springs g2 in forcing the actuating plate g away from transmission member c and in' moving the balance plate d, member e and coupling ring ,f into eccentric position. As a result of this resistance, these members do not immediately move into extreme eccentric position, but move rst into slightly eccentric position causing the shaft 3 thus to be driven slowly at the start. At the same time the pullofcentrifugal force on the members which are in slightly eccentric position, particularly the centrifugal pull on balance plate d, assists the action of the springs g2 in mbving the members further into eccentric position. The initial resistance imposed 1 by the driven shaft 3 is also reduced as its speed ing the centrifugal pull on the eccentric members will serve to oppose the action of the springsLgZ in keeping the actuating plate g spaced from primary transmission c and result in the eccentricity of membersfd, e," and f being reduced and thereby reducing the speed of shaft 3 in comparison with the speed of' the motor. Then, as

the motor speeds up, the eccentricity again tends to be increased, thereby again increasing the speed at which the shaft 3 is driven.

My construction shows a pair of clutch members (m and n) alternately holding and forcing the coupling ring f to rotate when in eccentric position, and another pair of clutch members (o and p) alternately acting to cause the driven shaft 3 to be rotated. It would be possible to increase the number of the clutch members in each of the two sets by changing lthe construction so as to provide additional concentric flanges orsurfaces fOr the additional clutch members, and by changing the construction of the coupling ring f accordingly. For example, if four clutch members were provided in each set, with two additional concentric anges on both the interior of housing section b and the inner end of driving shaft 3, coupling ring f would be made with four radial ribs f4 instead of two as shown, such radial ribs being equally spaced, in such case at right angles to each other, and coupling ring f would similarly be made with four radial guideways formed by guide anges f3 instead of two such guideways as shown, the radial guideways being also equally spaced with reference to each other, and with reference to the radial ribs f5, thus a radial guideway between each pair of radial ribs. The action would be similar to that already described, the clutch members in each set functioning alternately.

I have illustrated and described an eiiicient form of'construction for carrying my invention into effect, but do not wish to be limited to the precise details' of construction set forth, since these may be varied; and mere modifications of the elements of the following claims within the scope of my invention are intended to be included.

I claim:

1. A gearless variable speed transmission comprising a divided case, a driving shaft journaled in one section of said case and a driven shaft journaled in the other section of said case; a`

and out of eccentricity with the axis of rotation of said primary transmission member, thus into and out of active position; a coupling ring carried by said coupling member; the section of the case in which the driven shaft is journaled provided with spaced concentric surfaces, and said driven shaft within said case provided with similar spaced, concentric surfaces; clutch rings located between said concentric surfaces; mean cooperating with said concentric surfaces, holding said clutch rings. against rotation in one direction independently of said surfaces; said ,coupling ring andA said clutch rings operatively connected, said connection adapted, thru the medium of the members of one set of said clutch rings, acting alternately,l to cause said coupling ring, when in itseccentric position, to rotate in one direction, and thereby to transmit driving motion to the driven shaft thru the medium of the members of the other set of said clutch rings, acting alternately; and a manually operated control for the movement of said cou pling member and therewith said coupling ring into and out of eccentric, active position.

2. A gearless variable speed transmission comprising a divided case, a driving shaft journaled in one section of said case and a driven shaft journaled in the other -section of said case; a primary transmission member fast on said driving shaft; a coupling member carried by said primary transmission member and movable into and out of eccentricity with the axis of rotation ofsaid primary transmission member, thus into and out of active position; a coupling ring carried by said coupling member; the section of the case in which the driven shaft is journaled provided with two spaced.- opposed concentric surf' surfaces, holding said clutch rings against rotation in one direction independently of said surfaces; said coupling ring and said clutch rings operatively connected, said connection adapted,

thru the medium of the members. of one pair of said clutch rings, acting alternately, to causesaid coupling ring, when in its eccentric positin, ,to 'rotate in one direction, and thereby to transmit driving motion to the driven shaft thru the,

medium of the members of the other pair of said clutch rings, acting alternately; a manually oper-` ated control including a spring controlled actuating plate reciprocable axially relatively to vsaid primary transmission member, and connections between said actuating plate and said coupling member adapted to cause themovement of said coupling member, and with it said coupling ring into and out of eccentric position.

3. A gearless variable speed transmission comprising `a divided case, a driving shaft journaled in one section of said' case and a driven shaft journaled in the other section of said case; a primary transmission member fast on said driving shaft; two members carried by said primary transmission member and oppositely movable into and out of eccentricity with the axis of rotation of said primary transmission member, one of said members constituting a coupling member and the other constituting a balance plate; a coupling ring carried by said coupling member; the section of the case in which the 'driven shaft lis journaled provided with spaced concentric surfaces, and said driven shaft within said case provided with similar spaced concentric surfaces;

faces; means, cooperating with said concentric tion in one direction independently of said surfaces; said coupling ring and gsaid clutch rings operatively connected, said connection adapted, thru the medium of the memb'ers of one set of said-clutch rings, acting alternately, to cause said coupling ring, when in its eccentric position, to rotate in one direction, and thereby to transmit driving motion to the driven shaft thru the medium of the members of the other set of said clutch rings, acting alternately; a manually operated control including a. spring controlled actuating plate reciprocable axially relatively to said primary transmission member, and connections between said actuating plate and said balance plate and said coupling member adapted to cause surfaces, holding said clutch rings against rotaf the movement of said balance plate and said shaft; a coupling member carried by said pri-l mary transmission member and movable into and out of veccentricity with the axis of rotation of said primary transmission member, thus into and out of active position; a coupling ring carried by ,said coupling member; the section of the case in which the driven shaft is journaled provided with two vspaced opposed concentric surfaces, and

said driven shaft within said case provided with two similar spaced, opposed concentric surfaces;

a pair of clutch rings located between each of the.

two opposed concentric surfaces; means, cooper, ating with said concentric surfaces, holding said clutch rings against rotation in one direction independently of said surfaces: said-coupling ring ment of said coupling member and therewith said coupling ring into and out of eccentric, active position.

5. A gearless variable speed transmission comprising a divided case, a driving shaft journaled in one section of said case and a driven shaft journaled in the other section of said case; a

primary transmission member fast on said driving shaft; a coupling member carried by said primary transmission member and movable into and out of eccentricity with the axis of rotation of said primary transmission member, thus into and out of active position; a coupling ring carried by said coupling member; the section of the case in which the driven shaft is journaled provided with spaced concentric surfaces, and said driven shaft within said case provided with similar spaced concentric surfaces; clutch rings located between said concentric surfaces;,means, cooperating with said concentric surfaces, holding said clutch rings against rotation in one direction independently of said surfaces; said coupling ring and said clutch rings operatively connected,said connection adapted, thru the medium of the members of one set of said clutch rings, acting alternately, to cause said coupling ring, when in its eccentric position, to rotate in one direction, and thereby to transmit driving motion to the driven shaft thru the medium of the members of the other set of said clutch rings, acting alternately; a manually operated control including a spring controlled actuating plate reciprocable axially relatively to said primary transmission member, and connections between said actuating plate and said balance plate and said coupling member adapted to cause the movement of said balance plate and lsaid coupling member, and, with the latter, said coupling ring into and out of eccentric position. 6. A gearless variable speed transmission comprising a divided case, a driving shaft journaled in one section of said case and a driven shaft journaled in the other section ofsaid case; a

' primary transmission member fast on said drivconcentric surfaces; means, cooperating'with said concentric surfaces, holding said clutch rings against rotation in one direction independently of said surfaces; said coupling ring and said clutch rings operatively connected, said connection adapted. thru the medium of the members of one set of said clutch rings, acting alternately. to cause said coupling ring, when in its eccentric position, to rotate in one direction, and thereby to transmitvdriving motion to the driven shaft thru the medium oi' the members of the other set of said clutch rings, acting alternately; a`

manually operated control including a spring controlled operating plate reciprocable axially relatively to said primary transmission member, said actuating plate having perpendicular arms, and cooperating means provided on said arms and said coupling member, whereby the reciprocation of said actuating plate causes said coupling member and therewith said coupling ring, to be moved into and out of eccentric, active position.

7. In a variable speed transmission comprising a case and normally disconnected driving and driven shafts journaled in said case, the means -for transmitting motion from the driving to the driven .shaft comprising a primary transmission member fast on the driving shaft; a coupling member carried by said transmission member andV movable into and out of eccentricity with the axis of rotation thereof, thus into and out of active position; a coupling ring carried by said coupling member; a setvof independently rotatable .clutch rings associated with the case section in which said driven shaft is journaled, and another set of independently rotatable clutch rings associated with the driven shaft; operative connections b'etween certain of said clutch rings and said cou- 4pling ring adapted to cause said coupling ring to rotate, when in eccentric position, and by such rotation, thru ,the medium of the other clutch rings, to transmit driving motion to said driven shaft; and a manually operated control `for the movement of said coupling member and therewith said coupling ring into and out of eccentric, active position.

.8. In a variable speed transmission comprising a case and-normally disconnected driving and driven shafts journaled'in said case, and means for transmitting motion from lthe driving to the driven shaft comprising a primary`transmission member fast on the driving shaft; two members carried by said primary transmission member and oppositely movable into and out of eccenvtricity with the axis of rotation thereof, one of said members constituting a coupling member, the other a balance plate; a coupling ring carried by said coupling member; a set of independentlyrotatable clutch ringsassociated with the case section in which said driven shaft is journaled, and another set of independently rotatable clutch rings associated with the driven the medium of the other clutch rings, to transmit driving motion to said driven shaft; and a manually operated control for the movement of said coupling member and therewith said coupling ring into and out of eccentric, active position.

9. In a gearless speed transmission having a driving shaft and a driven shaft, a power transmitting connection between said shafts, comprising a primary transmission 'member fast on the driving shaft, a'coupling member carried by said primary transmission member, and movable into and out of eccentricity with the axis of `rotation of said primary transmission member, and thus into and out of active position, a coupling ring .carried by said coupling member, clutch means operatively connected with said coupling ring, and adapted `to cause said coupling ring to rotate when in eccentric position, at a speed relative to the eccentricity of said coupling ring, other clutch means operatively connected with said coupling ring adapted to cause said coupling ring, when rotated, to drive said driven shaft, and manually operable means adapted to cause the movement of said coupling member and therewith said coupling ring into eccentric, active position, or concentric, inactive position.

l0. In a gearless speed transmission having a driving shaft'and a driven shaft, a power transmitting connection between said shafts, comprising a primary transmission member fast on the driving shaft, a coupling member carried by said primary transmission member, and movable into and out of eccentricity with the axis of rotation of said primary transmission member, and thus into and out of active position, a coupling ring carried by said coupling member, clutch means operatively connecting said driving and driven shafts thru the medium of said coupling ring; said clutch means comprising two sets of clutch rings, those of one set alternately engaging and releasing said coupling ring, and those of the other set, in cooperation with said coupling ring, transmitting the driving motion to said driven shaft, the movements of said clutch rings and said coupling ring complementing each other,

`whereby to cause said driven shaft to receive substantially even motion; and manually operable means adapted to cause the movement of said coupling member and therewith said coupling ring into eccentric, active position, or concentric, inactive position.

11. A gearless'variable speed transmission comprising a divided case, a driving shaft journaled in one section of said case and a driven shaft journaled in the other section of said case; a primary transmission member fast on said driving shaft; a coupling member` carried by said primary transmission member and movable into and out of eccentricity with the axis of rotation of said primary transmission member, thus into and out of active position; a coupling ring carried by said coupling member; the section of the case in which the driven shaft is journaled provided with two spaced,l opposed concentric surfaces, and said driven shaft within said case provided with two similar spaced, opposed concentric surfaces; a pair of clutch rings located between each of the two opposed concentric surfaces; means, cooperating with said concentric surfaces, holding said clutch rings against rotation in one direction independently of said surfaces; said coupling ring and said clutch rings operatively connected, said operative connections comprising crank pin elements carried by said coupling ring, located equi-distant from the center of said coupling ring, and radial guideways in one pair of clutch rings inwhich said crank pin elements slidably bear, and crank pin elements carried by the other pair of clutch rings, located equi-distant from the center of rotation of thel latter mentioned clutch rings, and radial guideways in said coupling ring in which said latter mentioned crank pin elements slidably bear; said coupling ring and said clutch rings operatively connected,

said. operative. connections comprising crank pin elements carried Nby said ments slidably bear; one set of said clutch rings alternately engaging and releasing said coupling ring, and the other set of said clutch rings engaged by said coupling ring and transmitting motion to said driven shaft; the movements of said clutchvrings and said coupling ring cooperating with and complementing each other, whereby to cause said driven 'shaft to receive substantially even motion; the rate of said motion imparted to said driven shaft being determined by the extent of eccentricity of said coupling ring; a manually operated control including a spring controlledactuating plate reciprocable axially relatively to said primary transmission member, and connections betweensad actuating plate and said coupling member adapted to cause the movement of said coupling member, and with it said coupling ring, automatically into and out of eccentric position.

12. A gearless variable speed transmission comprising a divided case, a driving shaft journaled in one section of said case and a driven shaft journaled in' the other section of said case; a primary transmission member fast on said driving shaft; a coupling member carried by said primary transmission member and movable into and out of eccentricity with the axis of rotation of said primary transmission member, thus into and out ofv active position; a coupling ring carried by said coupling member; the section of the case in which the driven shaft is journaled provided with spaced concentric surfaces, and said driven shaft within said case provided with vsimilar spaced, concentric surfaces; clutchvv rings located between said concentric surfaces; means, cooperating with said concentric surfaces, holding said clutch rings 'against rotation in one direction independently of said surfaces; said coupling ring and said clutch rings operatively connected, said operative connections comprising crank pin elements carried by' said coupling ring, located equi-distant from the center of said coupling ring, and radial guideways in one set of clutch rings in which said crank pin elements slidably bear, and crank pin elements carried by the other set of clutch rings, located equidistant from the center of rotation of the latter mentioned clutch rings, and radial guideways in said coupling ring in which said latter mentioned crank pin elements slidably bear; said operative connections adapted, thru the medium of one set of clutch rings, acting alternately, to cause said coupling ring, when in eccentric position, to be rotated in one direction, and, thru the medium of the other set of clutch rings, acting alternately, to cause saiddriven shaft to be' rotated by said coupling ring when. the latter is rotated; the speed of rotation of said coupling ring, and thereby the speed of rotation `of said driven shaft, being determined by the extent of eccentricity of saidv coupling ring from the center of rotation of said primary transmission member; a manually operated control including a spring controlled operating plate reciprocable axially relatively to said primary transmission member, said actuating plate having perpendicular arms, and `cooperating means provided on said arms and said coupling member, whereby the reciprocation of said actuating plate causes said coupling member and therewith said coupling ring, to be moved into andv FERDINAND W. SEECK. 

